JP6503514B2 - Rotary Stirling cycle apparatus and method - Google Patents

Description

  The present invention relates generally to the field of Stirling cycle machines, and more particularly Stirling engines, coolers, heat pumps. More particularly, the present invention relates to a pistonless Stirling cycle that utilizes a rotary expander mechanism and a compressor mechanism.

  The Stirling cycle is a thermodynamic cycle that involves, among other things, cyclical compression and expansion of air or other gas (i.e., working fluid) at different temperatures, thereby converting thermal energy into mechanical work without value. Furthermore, it is also known that this cycle is reversible, which means that when mechanical power is supplied, the device can function as a heat pump or cooling machine, with corresponding heating or cooling, and poles. It means even performing low temperature cooling.

  More specifically, the Stirling cycle is a closed regenerative cycle that generally utilizes a gaseous working fluid permanently. Here, "closed-cycle" means that the working fluid is permanently enclosed in the thermodynamic system, and the term "regeneration" means internal heat exchange. Reference to the use of a so-called regenerator. The regenerator improves the thermal efficiency of the device by recycling internal heat that would otherwise be irreversibly passed through. The Stirling cycle, like many other thermodynamic cycles, consists of four major processes: (i) compression, (ii) heat application, (iii) expansion, and (iv) heat removal. However, in practical institutions, these processes are not separate but rather overlap.

  An example of a typical Stirling engine (engine) 10 having a crank drive is shown in FIG. Here, a single gas circuit is formed by two heat exchangers, ie two cylinders 12, 14 connected to one another via the channels of heater 16, regenerator 18 and cooler 20. The outer surface of the heater 16 has an elevated temperature by exposure to a high temperature environment, whose function is to transfer heat to the working fluid in the engine while the working fluid flows through the channels of the heater 16. The outer surface of the cooler 20 is exposed to a relatively cool environment, whose function is to release heat from the working fluid while it flows through the channels of the cooler 20.

  The regenerator 18 is introduced between 6 and the cooler 20 to avoid heat loss, otherwise it will cause heat loss if the heater 16 and the cooler 20 are in direct contact. The regenerator 18 of this embodiment has a porous medium enclosed within a metal casing. The porous medium should be formed of a material having high heat capacity, and ideally having infinite radial heat conduction and zero axial heat conduction. The porous medium can be understood as acting as a heat sponge, transferring heat to the regenerator material, and storing heat as the working fluid flows from the "hot" zone to the "cold" zone. As the working fluid flows in the reverse direction, the accumulated heat returns from the regenerator to the working fluid. Insulating materials are usually used to isolate the porous media from the walls of the casing to reduce heat loss.

  Most of the working fluid during the heat removal phase is cold zone (ie, the cold cylinder 14 and the cooler 20) to supply most of the working fluid to the hot zone (ie, the heat cylinder 12 and the heater 16) during the heat input phase. The piston 22 in the thermal cylinder 12 normally precedes the piston 24 of the cold cylinder 14 by 90.degree. To 110.degree. Of displacement to supply the heat cylinder 12, the volume of the thermal cylinder 12 is Lead by an angle of 90 ° to 120 ° to the volume.

  FIG. 2 a shows an exemplary graph of the change in volume (variation) in the thermal cylinder 12 (dashed line) and an exemplary graph of the change in volume of the cold cylinder 14 (solid line).

  Two variable volumes (heat and cold) connected by a set of heat exchangers (heater 16, regenerator 18 and cooler 20), a thermal space preceded by 90 ° to 110 ° with respect to volume variations of the cold space Volume fluctuations and the back and forth flow of the working gas between the variable heat space and the cold space via the channels of the set of heat exchangers 16, 18, 20 are characteristic of the Stirling cycle machine. A typical PV graph of variable thermal or expanded volume (dashed line) and variable cold or compressed volume (solid line) is shown in FIG. 2b.

  Thus, when the heater 16 is exposed to a relatively high temperature environment and the cooler 20 is exposed to a relatively low temperature environment, the machine exerts a force (ie, the heat or expansion space area is a cold or compressed space area (See Figure 2b), which functions as an engine.

  However, if the cooler 20 is exposed to a relatively cool environment and the piston is driven using an electric motor (e.g., via a shaft) or other actuation source, within the heat exchanger 16 and the variable expansion space 12 The temperature of the working fluid at the point is significantly reduced (eg, reduced to cryogenic levels), which causes the machine to act as a cooling device to generate low temperature (ie, the expansion space area in small).

  Alternatively, the heat removal temperature in the cooler 20 if the heat exchanger 16 is exposed to a relatively cool environment and the piston is driven using an electric motor (eg via a shaft) or other actuation source Is considerably higher than the temperature of the heat exchanger 16, and the machine operates as a heat pump (ie absorbs heat at low temperatures and distributes heat at high temperatures).

  The cycle of a conventional Stirling machine in which the pistons reciprocate in the cylinder is usually completed after a shaft angle of 360 °.

However, the cycle of a conventional Stirling machine (kinematic drive engine or free piston reciprocating machine) in which the pistons reciprocate in the cylinder has, for example, the following considerable disadvantages:
A relatively large volume and large specific area of the in-cylinder variable volume which results in greater machine weight and dimensions;
The relatively large volume and weight of the crankcase, and the complexity of the crank drive or other type of kinematic drive mechanism;
A relatively low rotational speed of the shaft in a free piston machine or a relatively low linear velocity of the piston resulting from a piston reciprocating frequency
There is a drawback of that.

  In order to reduce the size and weight of these machines, designers use the “seal” of vertical rod articulated pistons and drive mechanisms (ie so-called non-pressurized crankcases) to separate the crankcase into the engine's gas circuit. can do.

  Such a seal has only been achieved for a very limited number of Stirling machines, and even for those engines, the working fluid in the internal gas circuit can completely eliminate the working fluid leak in the rod seal Because it can not be done, it must be replenished repeatedly.

  Furthermore, in a free piston machine there is no conventional drive mechanism, and the piston is reciprocated using gas forces and mechanical springs that occur in the internal gas circuit of the machine. The reciprocating vibration of the cold piston can be converted to electrical power by attaching a rare earth magnet surrounded by a copper coil to the piston (ie, a linear generator). Such machines do not have a large crankcase and the engine is completely sealed by placing a linear alternator in the engine casing. Although their inherent weight and size have been improved significantly over those of conventional kinematic machines, so far the power output has been limited to about 3 to 10 kW (kilowatts), which corresponds to that of conventional movements Considerably lower than the output of the scientific engine. The piston reciprocating frequency corresponds to a shaft rotational speed of 2000 to 4000 RPM (revolutions per minute).

  The solution to the problem in reciprocating piston machines is believed to be in rotary machines. Therefore, much effort was put into development of the rotary Stirling engine / machine.

  For example, US Patent Application Publication No. 13/795, 632 discloses a set of "hot" and "cold" gerotors attached to the same shaft and separated from each other by a thermal barrier. Describes the Stirling cycle engine used. The barrier allows gas flow and thus provides a regeneration gas path connecting displacement chambers in a set of "hot" and "cold" gerotors. Gerotor type Stirling cycle engines can be used to generate electrical or mechanical power.

  U.S. Patent Application Publication No. 05 / 790,904 describes another embodiment of a Stirling cycle machine having a rotating mechanism. In this particular design, a rotary vane expander and a rotary vane compressor are mounted on the same shaft, where each vane unit defines four working volumes. The expander and the corresponding working volume of the compressor are connected via a set of heat exchangers provided in the expander casing and in the shaft.

  All these prior art embodiments have the same basic features of the Stirling cycle machine, that is to say the characteristic of harmonic fluctuations or approximate harmonic fluctuations by continuously connecting corresponding working spaces in the expander and compressor units. There is. Thus, after connecting each chamber by a set of heat exchangers, the working gas flows to reciprocate between corresponding working spaces. However, those skilled in the art will find that the above-mentioned rotation mechanism is very complicated and has the disadvantages of the rotation mechanism itself.

  Thus, rotating mechanisms such as twin screw or scroll mechanisms have been considered for use in Stirling cycle machines. The twin screw mechanism, in particular, has been a very common option for compressors. FIGS. 3A to 3D show, for example, the entire cycle of the twin screw compressor 30. FIG. During operation (i.e., during rotation of the twin screw shaft), the two intermeshing, counter-rotating male and female rotors rotate within the corresponding lobes and surrounding casing 34 between the working fluid 32 (e.g. Capture). It is forced axially forwardly by the interlocking male and female lobes, thereby gradually reducing the volume of the chamber created by the interlocking male and female lobes and compressing the trapped gas.

  As shown in FIG. 3, (a) the gas 32 is taken from the intake port 36, (b) the gas 32 is then captured and axially displaced, (c) this gas is produced by the intermeshing lobes Compressed by the decreasing chamber volume, (d) gas 32 is exhausted from exhaust port 38.

  FIGS. 4 (a)-(d) show alternating rotation mechanisms that can be used to compress or expand the working fluid, and in particular, FIG. 4 shows two nested identical ones rotating 180 ° with respect to the other A scroll compressor 40 comprising scrolls 42, 44 is shown. In the classical design, both scrolls 42, 44 are circular involute curves, and one scroll 42 or spiral is rotatable and orbits in the path defined by the matching fixed scrolls 44. The fixed scroll 44 can be fixed to the compressor body and the orbiting scroll 42 can be coupled to the crankshaft so that the orbiting motion produces a series of gas pockets moving between the two scrolls 42,44. The pockets formed draw in gas, move the gas from the outer portion of the scroll 42, 44 to the central portion, and exhaust the gas at this central portion. As the gas moves towards the center, the pocket volume decreases and its temperature and pressure increase to the desired discharge pressure. Both the scroll mechanism and the twin screw mechanism can also operate in the reverse mode, i.e. can operate as an expander simply by reversing the direction of rotation.

  Another example of a rotary mechanism used for gas compression or expansion is a conical screw rotary compressor 50 (eg, manufactured by Vert Rotors) as shown in FIG. The mechanism comprises a rotating inner rotor 52 and a rotating outer rotor 54. The inner and outer rotors 52, 54 are driven by the electric motor via a synchronization mechanism. The rotational movement of both the inner and outer rotors 52, 54 causes the gas to move along the rotational axis to displace and compress the gas. In operation, low pressure gas is supplied to the inlet at the large diameter side 56 and then compressed to a higher pressure and discharged from the outlet at the small diameter side 58. The rotation mechanism 50 can also be reversed for use as an expander. In FIG. 5, two different geometries of a conical screw rotary compressor are shown: (a) 2 + 3 profiles (contours) and (b) 3 + 4 profiles (contours).

  However, the periodic volume change provided by the twin screw, scroll, or conical screw type rotation mechanism follows a linear or non-linear sawtooth function as shown in FIG. The example of the volume change of the working fluid in expansion (positive slope part) and during compression (negative slope part) is shown. Here, the loose slope is defined by a linear function (i.e. a straight line) but can also be described by a non-linear function (e.g. a harmonic function or part of an anharmonic function).

  The sawtooth nature of the working fluid volume variations provided by these rotary machines has been formed by mechanisms not suitable for use in the Stirling cycle, however, a twin screw, scroll or conical screw mechanism.

  Currently available thermodynamic devices utilizing either twin screw or scroll mechanisms are supplied with a Rankine Cycle or Joule / Brighton Cycle, each requiring only one working fluid axial flow . For example, Patent documents 3 or 4 (DE 101 23 078 or Austrian patent 412 663) describe a thermodynamic cycle utilizing a twin screw expander.

  In particular, DE 101 23 078 A1 describes a machine which operates in a closed thermodynamic cycle and is supplied with high pressure gas by means of a twin screw mechanism and is also expanded. The work resulting from the gas expansion is converted to useful mechanical work by the rotating twin screw shaft, and then the working fluid is reheated (or repressurized) back to the twin screw mechanism that repeats the cycle. .

  Other examples of rotary thermodynamic engines (using the scroll mechanism) can be found in Non-Patent Document 1 (a publication by Youngmin Kim) by Yunmin Kim, Donkil Shin, Yanhi Lee, and Kwen Park. Gas flow is described in Dongkil Shin, Janghee Lee and Kwenha Park ("Noble Stirling engine employing scroll mechanism", Proceedings of the International Stirling Engine Conference, 19-21 September 2004, pp. 67-75). A simple analysis reveals that so-called Stirling engines actually operate in a closed Joule / Brighton cycle, as they circulate in one direction and not in reciprocating motion.

US Patent Application Publication No. 13/795, 632 US Patent Application Publication No. 05 / 790,904 DE 10123078 Specification Austrian Patent No. 412663

publication by Youngmin Kim, Dongkil Shin, Janghee Lee and Kwenha Park (“Noble Stirling engine employing scroll mechanism”, Proceedings of the 11th International Stirling Engine Conference, 19-21 September 2004, pp. 67-75)

  Thus, the object of the present invention is to provide a mechanism of rotary expanders and rotary compressors, eg twin screw, scroll, even if the applied working fluid volume change is based on a linear or non-linear sawtooth waveform. It is an object of the present invention to provide a Stirling cycle device which can utilize a conical screw mechanism. Furthermore, a particular object of the present invention is to obtain a rotary Stirling cycle cooler which can be smaller than currently available Stirling cycle coolers and which has an improved efficiency.

  Preferred embodiments of the present invention aim to overcome one or more of the above mentioned disadvantages of the prior art.

According to a first embodiment of the present invention, a Stirling cycle device is provided, which comprises:
A sealable housing,
A first rotational displacement unit is in fluid communication with a second rotational displacement unit, each unit operably mounting each unit in a separate fluid tight portion in the housing, at least one thermodynamic state of the working fluid during use The first and second rotational displacement units adapted to generate a periodic change of a parameter, each of the first and second rotational displacement units being
A compressor mechanism, comprising: a first compressor working chamber capable of receiving a first portion of the working fluid; and at least a second compressor working chamber capable of receiving a second portion of the working fluid, the first compressor working The compressor mechanism having a first outlet port and the second compressor operating chamber having a second outlet port;
An expander mechanism, comprising: a first expander actuation chamber capable of receiving the first portion of the working fluid; and at least a second expander actuation chamber capable of receiving the second portion of the working fluid; The expander mechanism, wherein the first expander working chamber has a first inlet port, and the second expander working chamber has a second inlet port.
A drive coupling assembly operable to operatively couple the first expander mechanism to the first compressor mechanism,
The rotation of the first and second rotational displacement units between the first compressor working chamber and the first expander working chamber, and between the second compressor working chamber and the second expander working chamber The drive coupling assembly having a rotary valve mechanism capable of causing a predetermined sequence of periodic fluid exchange at predetermined intervals of an angle,
The first and second rotational displacement units, including
An actuator operatively coupled to the first and second rotational displacement units, wherein the rotational movement of the first rotational displacement unit is linked to synchronize with the second rotational displacement unit, thereby using Wherein the first predetermined period change of the at least one thermodynamic state parameter of the working fluid is offset by a predetermined phase angle with respect to the second predetermined period change of the at least one thermodynamic state parameter of the working fluid The actuator, which can be
Equipped with

  The device according to the invention is a conventional sterling of linear or non-linear "sawtooth" periodic variations of at least one thermodynamic state parameter in the corresponding rotary compressor and expander mechanisms of two rotary displacement units. It offers the advantage of being able to be paired and combined to produce an overall variation of the working space volume that closely follows the periodic harmonic function typical of a cycle machine (e.g. piston movement). It provides a true rotary Stirling cycle device that is simpler and, in particular, has improved efficiency and performance when in compact form. The invention can operate to perform mechanical work, but can also operate reversibly as a cooler or heat pump.

  Advantageously, the first drive connection assembly further comprises at least one first drive shaft and an inner wall, at least one further configured to operably surround the at least one first drive shaft. It can have one first shaft casing.

  Advantageously, the at least one first shaft casing extends over the first circumferential segment of the inner wall and is respectively provided at a corresponding predetermined first axial position, axially spaced from one another and A plurality of first fluid channels extending partially in the circumferential direction and a second circumferential segment of the inner wall are provided at corresponding second predetermined axial positions, respectively, axially relative to one another. And a plurality of second fluid channels spaced apart and partially extending in the circumferential direction, and the first circumferential segment is provided radially opposite to the second circumferential segment In addition, each of the first axial positions is axially offset from each of the second axial positions.

  Preferably, the first fluid channel and the second fluid channel spaced apart from each other in the axial direction and partially extending in the circumferential direction can exist over an angle larger than 180 °.

  Advantageously, the at least one drive shaft has a first conduit having a first opening fluidly connected to the first outlet port and a second conduit having a first opening fluidly connected to the first inlet port. A first set of two mutually corresponding conduits may be provided, each of the mutually corresponding first and second conduits radially exiting the drive shaft at a predetermined first radial angle. One of the two second openings axially adjacently connected to each other and having two second openings axially connected to each other is one of the plurality of first fluid channels. And the other of the two second openings axially adjacently connected to each other is in fluid communication with one of the plurality of second fluid channels. It can be assumed to be.

  More preferably, the at least one drive shaft has a first conduit having a first opening fluidly connected to the second outlet port and a second opening having a first opening fluidically connected to the second inlet port. The conduit comprises at least a second set of two mutually corresponding conduits, each of the corresponding ones of the first and second conduits being each other being radially spaced from the drive shaft at a predetermined first radial angle. One of the two second openings axially adjacently connected and having two second openings connected adjacent to each other in the axial direction is one of the first fluid channels and one of the plurality of first fluid channels. The other of the two second openings which are fluidly engageable and axially adjacent to each other are in fluid communication with one of the plurality of second fluid channels. It can be assumed to be engaged.

  More preferably, each of said plurality of first fluid channels is in fluid communication with a corresponding one of said plurality of second fluid channels, and, in use, said first compressor actuation chamber and said first expander actuation Heat exchange with the chamber and between the second compressor operating chamber and the second expander operating chamber can be enabled in a predetermined sequence.

  Advantageously, the first compressor working chamber and the first expander working chamber fluidly connected in the first rotational displacement unit, and the second compressor working chamber and the second expander working chamber fluidly connected. For each, a first working space and a second working space may be formed.

  Advantageously, the first compressor working chamber and the first expander working chamber fluidly connected in the second rotational displacement unit, and the second compressor working chamber and the second expander working chamber fluidly connected. For each, a first working space and a second working space may be formed.

  Advantageously, the first working space and the second working space of the first rotary displacement unit are respectively in fluid communication with the corresponding working spaces of the first working space and the second working space of the second rotary displacement unit. be able to.

  Preferably, each of the correspondingly fluidly connected first fluid channel and the second fluid channel of the first rotational displacement unit is associated with the correspondingly fluidically connected first fluid of the second rotational displacement unit. A fluid communication can be made with one fluid channel corresponding to the channel and the second fluid channel respectively.

  Advantageously, the correspondingly fluidly connected first fluid channel of the second rotary displacement unit and the correspondingly fluidically connected first and second fluid channels of the first rotary displacement unit respectively The fluid communication between each of the channel and the second fluid channel may comprise any one of a first heat exchanger, a regenerator, and a second heat exchanger or any serial combination thereof .

  Preferably, the first heat exchanger can supply heat to the working fluid, and the second heat exchanger can remove heat from the working fluid. This allows the device to operate in different modes, eg as a cooler or as a heat pump, depending on where the first and second heat exchangers are arranged in combination with the regenerator Bring the benefits of being able to

  More preferably, the regenerator can be fluidly connected between the first heat exchanger and the second heat exchanger.

  Alternatively, the first heat exchanger may be an integral part of the first rotational displacement unit, and / or the second heat exchanger may be an integral part of the second rotational displacement unit.

  Preferably, each of the first rotational displacement unit and the second rotational displacement unit may have a twin screw mechanism.

  Alternatively, each of the first and second rotational displacement units may have a scroll mechanism or a conical screw mechanism.

  In another alternative embodiment, each of the first rotational displacement unit and the second rotational displacement unit may have any one of a twin screw mechanism, a scroll mechanism, or a conical conical screw mechanism.

  Advantageously, the actuator may comprise a motor and a transmission capable of synchronously driving the first and second rotational displacement units.

  Alternatively, the actuator may comprise a motor and a transmission which may be powered by any one of the first and second rotational displacement units.

  Advantageously, the compressor mechanism and the expander mechanism of the first rotary displacement unit and the compressor mechanism and the expander mechanism of the second rotary displacement unit are respectively provided in separate and sealed parts of the housing. be able to.

  Preferably, the first rotational displacement unit may be a compression unit, and the second rotational displacement unit may be an expansion unit. Alternatively, the first rotational displacement unit is an expansion unit and the second rotational displacement unit is a compression unit, based on the application of the device, ie the heat pump, the cooling or the application as an engine. can do.

  Preferred embodiments of the invention are described below by way of example only and not limitation and with reference to the accompanying drawings.

Fig. 6 shows a kinematically driven Stirling engine with "hot" and "cold" cylinders, a heater, a cooler, and a regenerator. (a) is a graph of "hot" in-cylinder volume change (dashed line) and "cold" cylinder in-cylinder volume change (solid line), and (b) is a PV graph of "heat" cylinder in Stirling cycle engine (Dashed line) and PV graph of "cold" cylinder (solid line). (a)-(d) show a twin screw compressor and its operation state. The schematic and operating principle of the scroll mechanism compressor are shown, (a) shows the scroll mechanism in the maximum filling position, (b) shows the scroll mechanism in the inlet shutoff state, and (c) shows the scroll mechanism at the start of discharging. And (d) show the scroll mechanism at the end of the discharge. Fig. 3 shows an example of a conical screw rotary compressor with two different geometries: (a) 2 + 3 profiles (contours) and (b) 3 + 4 profiles (contours). Fig. 7 shows a linear sawtooth waveform representing volume change during expansion (positive slope) and during compression (negative slope). Fig. 6 shows an isometric view from the side of the "expansion" or "cold" unit in an embodiment of the device according to the invention. Fig. 6 shows an isometric view from the side of the "compression" or "warm (or heat)" unit in an embodiment of the device of the invention. Fig. 8 shows an isometric view, partly in cross section, of the device shown in Fig. 7; FIG. 8 shows an isometric view of two coupled twin screw mechanisms of the apparatus shown in FIGS. 7 and 8, each twin screw mechanism having a compression chamber and an expansion chamber. FIG. 1 shows an isometric view of one rotor in a twin screw mechanism, which includes an internal conduit (dashed line) and an outlet / inlet. FIG. 8 shows a schematic cross-sectional view of a rotary unit (such as the device shown in FIG. 7) having an internal compression / expansion chamber. FIG. 7 shows an enlarged cross-sectional view of the shaft exposing the internal conduit of the rotary valve mechanism. FIG. 6 shows a cross-sectional view of a male rotor shaft in a twin screw mechanism. FIG. 14 is a top view of the male rotor shaft of FIG. 13 showing the opening of the inner conduit. FIG. 6 shows an isometric cross-sectional view of a portion of a casing of a rotary valve mechanism having circumferential and axial offset fluid channels. FIG. 6 shows an enlarged cross-sectional view of a fluid channel and sealing ring adjacent to it disposed in a casing surrounding the rotor shaft of the rotary valve mechanism. FIG. 5 shows an enlarged cross-sectional view of a detail of a rotary valve assembly consisting of a shaft, a casing and a conduit. Fig. 2 shows pipes connecting the corresponding compressor space and expander space in the (a) "cold" rotational displacement unit and (b) the "warm" rotational displacement unit of the device according to the invention. FIG. 2 shows a schematic view of the fluid connection between two corresponding working spaces in a “cold” rotational displacement unit and a “warm” rotational displacement unit. Fig. 6 shows a graph of the volume variation in the first chamber of the compressor (solid line) and the expander (dashed line) in the "cold" unit. Fig. 6 is a graph of volume variation in the first chamber of the "cold" unit, showing the formation of two working spaces. Fig. 6 shows a graph of paired working space volume variations in the "cold" unit (solid line) and the "warm" unit (dashed line). FIG. 23 is a graph of the sum of paired working space volume variations of FIG. 21. FIG. Fig. 6 shows PV graphs in the expansion space (solid line) and the compression space (dashed line) of the cooling Stirling cycle device of the present invention. Fig. 6 shows a twin screw mechanism for the inventive Stirling cycle device in a multi-block configuration, in which either a single common male or female rotor is disposed between corresponding female or male rotors. Fig. 14 shows an alternative set of twin screw mechanisms utilizing a three lobed rotor. Fig. 14 shows another alternative set of twin screw mechanism utilizing a four lobed rotor. FIG. 10 shows another embodiment of a rotary valve assembly, wherein an isometric view of the rotary valve assembly is provided with a peripheral fluid channel on the rotary drive shaft. FIG. 29 illustrates a cross-sectional view of another embodiment of the rotary valve assembly of FIG. 28. FIG. 30a shows an isometric view of a portion of the drive shaft exposing peripheral fluid channels provided on the outer surface of the drive shaft and the inner conduit. FIG. 30b shows a side view of a portion of the drive shaft exposing peripheral fluid channels provided on the outer surface of the drive shaft and the inner conduit. FIG. 30 c shows a cross-sectional view of a portion of the drive shaft exposing peripheral fluid channels provided on the outer surface of the drive shaft and the inner conduit. In an alternative embodiment utilizing the scroll mechanism of the device of the invention, the "cold" and "warm" units are fluidly connected via a heat exchanger assembly (cold exchanger, regenerator, warm exchanger) FIG. 2 shows a schematic view of the present embodiment.

  An exemplary embodiment of the invention is described for a rotary Stirling cycle cooler. However, it should be understood that, generally, the inventive Stirling cycle device works equally well in Stirling engine mode (i.e. mechanical work output) or heat pump (heat output).

  In addition, male and female screw rotors that mesh with one another can be provided with different lobe number ratios. Logically, this ratio starts with "1" (i.e. "2/2"), but it is also possible to use special other (e.g. larger) ratios. Typical examples of the ratio actually used may be "3/4", "3/5", "4/6", "5/7", "6/8" and so on. Furthermore, the screw lobes can have a symmetrical or asymmetrical profile. For the purpose of merely illustrating the basic principles of the present invention, the exemplary embodiment provides a simpler symmetric profile (contouring) with a "2/2" ratio (ie, this ratio is equal to "1") lobes. Equipped with a screw rotor. Furthermore, one skilled in the art will appreciate that optimum performance can only be achieved utilizing any other (i.e. more suitable) ratio and / or lobe profile (asymmetric or symmetrical). However, the basic principles of the present invention are applicable to any suitable lobe number ratio and lobe profile.

  Referring to FIGS. 7-11, a first embodiment of the Stirling cycle apparatus of the present invention, which is an "expanding" or "cold" unit 102, and "compression" or "warm". ) Unit 104 is provided. Each of the “cold” unit 102 and the “warm” unit 104 further includes a compressor mechanism 106 and an expander mechanism 108. The 'cold' unit 102 and the 'warm' unit 104 are in fluid communication via four sets of heat exchangers, each set comprising a 'cold' heat exchanger 110, a regenerator 112, and A "warm" heat exchanger 114 is included. Each of the "cold" unit 102 and the "warm" unit 104 has twin screw mechanisms 116, 118, which are shown by the twin screw rotors 120, 122 shown in FIGS. Become. Each twin screw mechanism 116, 118 has a compression part 124, 128 and an expansion part 126, 130. The corresponding compression parts 124, 128 and expansion parts 126, 130 in the male rotor 120 and the female rotor 122, respectively, are coupled by a single drive shaft 132, 134, the coupling being such that the expansion parts 126, 130 are compression parts. It carries out so that it may become the mirror symmetry same as 124,128.

  Furthermore, each of the two compression parts 124, 128 and the two expansion parts 126, 130 are arranged in an enclosure 136 which is itself sealed (see FIG. 11).

  A motor (not shown) and a transmission (not shown) are each operatively coupled to a corresponding twin screw mechanism 116, 118, in this case provided as a drive coupling assembly within the transmission (eg, box 138) A meshing gear is used to synchronize the male rotor 120 and the female rotor 122. Box 138 further includes an actuator (ie, an efficient and controllable electric motor) that can drive the twin screw mechanism via the transmission. Alternatively, the transmission (i.e. bearings, gear mechanism) can be arranged in a different part of the housing, for example in a casing 140 which encloses the shafts 132, 134 of the twin screw mechanism 116, 118.

  Referring now to FIGS. 10, 12, 13 and 14, a set of corresponding conduits 144, 146, 148, 150 is provided in the shaft 132 of the male rotor 120. At the high pressure end of the compression part 124 and the low pressure end of the expansion part 126, radially arranged fluid ports 152 are provided between two adjacent lobes of the male screw rotor 120, as shown in FIGS. As shown in detail, fluid connections are made to the corresponding conduits in the set of conduits 144, 146, 148, 150 (which are axially internal cylindrical channels). Each of the fluid conduits 144, 146, 148, 150 has a first outlet 154 and a second outlet 156, and the first and second outlets in each of the fluid conduits 144, 146, 148, 150 are arranged adjacent to each other Ru.

  Referring now to FIGS. 15, 16 and 17, the first set of fluid channels 158 (i.e., slots) circumferentially extending partially in a large fan-like shape over a central angle greater than 180.degree. The first portion of the casing surrounding the shaft 132 of the rotor 120 is formed in a corresponding predetermined axial position (see FIG. 15). A second portion of the casing surrounding the shaft 132 of the male rotor 120 with a second set of fluid channels 160 (i.e., slots) extending in a large fan-like shape and partially extending circumferentially over a central angle greater than 180 °. The first portion of the casing is radially opposed to the second portion of the casing (see FIG. 15). Further, each of the first set of circumferentially partially extending fluid channels 158 is axially offset from each of the second set of circumferentially partially extending fluid channels 160.

  As shown in FIG. 17, each first outlet 154 is arranged to be fluidly connected only to each of the first set of circumferentially partially extending fluid channels 158, and each second outlet 156 is circumferentially It is arranged to be fluidly connected only to each of the second set of fluid channels 160 extending partially in the direction.

  As shown in FIG. 16, all fluid channels 158, 160 are separated by an "O" shaped seal ring 161, which is disposed in the portion of the casing surrounding the shaft 132. Furthermore, suitable seal arrangements can be applied to reduce potential gas leakage at the gap between the rotors or between the rotor and the casing. For example, the grooves extending along the ridges of the lobes can be provided with sealing strips, or Teflon and other suitable sealing materials which close any gaps can be used as sealing strips. In addition, the materials used to make the male and female rotors, casings or heat exchangers (e.g. non-metallic materials) can be made different based on the temperature used for the Stirling cycle .

  Referring to FIGS. 18 (a) and 18 (b), in each of the “cold” unit 102 and the “warm” unit 104, each of the first set of fluid channels 158 is via fluid connection 162 (eg, a pipe) Fluidly connect to corresponding portions of the second set of fluid channels. Each of the fluid connections 162 in the “cold” unit fluidly connects to the corresponding fluid connection 162 of the “warm” unit via the pipe 164. As noted above, a series of “cold” heat exchangers 110, regenerators 112 and “warm” heat exchangers 114 fluidly connect to the fluid path of each pipe 164.

  Referring to FIGS. 19-24, during operation of the inventive device 100 (i.e., in the cooling mode), the drive shafts 132, 134 of the two twin screw mechanisms 116, 118, respectively, provide motors and transmissions (not shown). Synchronized rotation through. The lobes of the corresponding male and female rotors 120, 122 mesh to form two compression chambers and two expansion chambers for the "cold" unit 102 and the "warm" unit 104 respectively (ie, 2 Lobe screw rotors form two separate chambers).

  The volume variation in one of the chambers of the compression part 128 (ie, chamber 1) and one of the chambers of the expansion part 130 (ie, chamber 1) in the “cold” unit 102 is shown in FIG. The compression volume variation 166 is identical to the expansion volume variation 168, but this volume variation is due to the mirror-symmetrical pair of twin screw rotors located at opposite ends of the twin screw mechanism 118 of the "cold" unit 102. As formed, the volume change 168 is out of phase with the volume change 166 (see FIG. 20).

  The following is a description of the individual processes that occur in the device 100 of the present invention. A first working space 170 is formed during reciprocating compression and expansion of the working fluid (i.e. gas) trapped in the compression part 128 of the twin screw mechanism 118 of the "cold" unit 102 and the chamber 1 of the expansion part 130. Also, during the reciprocating compression and expansion of the working fluid (i.e., gas) trapped in the compression part 128 of the twin screw mechanism 118 of the "cold" unit 102 and the chamber 2 of the expansion part 130, the second working space 172 is It is formed. Similar first and second working spaces (not shown) are formed by the twin screw mechanism 116 of the "warm" unit 104.

  In order to simplify the description of the process, the chamber 1 of the "cold" unit 102 is considered as a representative example for this embodiment in a cooling machine. The entire cycle (360 ° rotation of the twin screw rotors 116, 118) can be divided into three distinct phases.

Phase 1
The duration is from 0 ° rotation of the shafts 132, 134 to the beginning of the overlapping portion of circumferentially extending fluid channels 158, 160 offset from one another. Here, each first set of fluid channels 158 remains aligned with the corresponding first outlet 154. The first set of fluid channels 158 is fluidly connected to the second set of corresponding fluid channels 160 by the external fluid connection 162 (see FIG. 18). Furthermore, the second fluid channels 160 are not aligned from their respective second outlets 156 (see FIGS. 12 and 19). Basically, the aforementioned paired fluid channels 158, 160 and the corresponding axially offset first and second outlets 154, 156 function as a rotary valve mechanism, which is the chamber 1 Expansion part 130 and compression part 128 can be separated and connected in a timely manner. Thus, during the first phase, the gas located in chamber 1 of expansion part 130 in “cold” unit 102 continues to be expanded to approximately half of full expansion and is also located in chamber 1 of compression part 128 in “cold” unit 102 The gas continues to be compressed to about half of full compression.

Phase 2
The duration is from the start of the overlap of circumferentially extending fluid channels 158, 160 offset from one another to the end of the overlap. Near the middle of the cycle, a fluid connection occurs between the volume of chamber 1 in compression part 128 and the volume of chamber 1 in expansion part 130. The duration of this phase is predetermined by a predetermined overlap between the two axially offset and circumferentially partially extending first and second sets of fluid channels 158, 160. Accurate overlap “smooses” gas exchange between the volumes of chamber 1 in compression part 128 and expansion part 130, ie, minimizes or avoids pressure shocks between compression part 128 and expansion part 130. Make it even better.

Phase 3
The duration is from the end of the overlap to the full 360 ° of the cycle. During this phase, each second set of fluid channels 160 remains aligned with the corresponding second outlet 156. As mentioned in the description of phase 1, each first set of fluid channels 158 is fluidly connected by an external fluid connection 162 to each respective second set of corresponding fluid channels 160 (see FIGS. 18 and 19) . The first fluid channels 158 are not aligned from the corresponding first outlets 154. Thus, the gas located in chamber 1 of expansion part 130 in “cold” unit 102 continues to be expanded to approximately half of full expansion, and the gas located in chamber 1 of compression part 128 in “cold” unit 102 is completely Continue to be compressed to almost half of the compression.

  As mentioned above, after the overlap period is complete, the gas volume that continues to be compressed in the compression part 128 during the first half of the cycle will expand in the expansion part 130 during the second half of the cycle. At the same time, the gas volume continuing to expand in the expansion part 130 will be subjected to the compression process in the compression part 128 during the second half of the cycle. Therefore, the magnitudes of the volume fluctuations in the two formed working spaces 170 and 172 are substantially the same (see FIG. 21). In addition (as described above), since the rotors 120, 122 of the twin screw mechanism 116, 118 have two lobes, each of the first and second fluid channels may be replaced by another conduit set (e.g. By combining the corresponding first and second outlets of the one corresponding conduit set 144, 146, the second corresponding conduit set 148, 150), two equivalent working spaces can be provided in the chamber 2 of the expansion part 130 and the compression part 128. Is formed against. As a result, with respect to the two-lobe twin screw mechanism 116, 118, there are generally four working spaces formed in the "cold" unit 102 and four working spaces aligned in the "warm" unit 104. There is.

  FIG. 19 is a simplified schematic of the “cold” unit 102 and the “warm” unit 104, and the corresponding fluid connections (via a series of heat exchangers 110, 114 and regenerator 112) between the two working spaces Indicates

  Furthermore, volume variations in each working space of the "warm" unit 104 "follow" volume variations of the corresponding paired working spaces in the "cold" unit 102, but with a shaft angle of 90 ° to 120 ° (phase Angle) with delay. In this particular embodiment of the invention, the volumetric variation of each working space of the "warm" unit 104 has a delay of 90 ° to the volumetric variation of the corresponding working space in the "cold" unit 102. To "follow". However, those skilled in the art may use other phase angle delays between the "cold" unit 102 and the "warm" unit 104 to control the output (e.g., cooling output) of the Stirling cycle apparatus 100. Can.

  A variation graph of the volume 174 of the correspondingly paired working space in the “cold” unit 102 and the volume 176 of the paired working space in the “warm” unit 104 is shown in FIG. The rotation of the twin screw mechanism 116 in the “warm” unit 104 is offset by 90 ° with the twin screw mechanism 118 of the “cold” unit.

  FIG. 23 shows a total 178 of two pairs of working volumes 174, 176 for two pairs of working spaces. The sum 178 of the two pairs of working volumes 174, 176 closely approximates the variation of working space in a conventional Stirling engine (see FIG. 2a). Thus, when connecting the paired working spaces in the "cold" unit 102 to the paired working spaces in the "warm" unit 104 (via the set of heat exchangers 110, 114 and regenerator 1122), Stirling cycle cooling Apparatus 100 can be implemented. Because there are four working spaces in the "cold" unit 102 and four working spaces in the "warm" unit 104, the Stirling cycle cooler has the equivalent of four separate gas circuits, each of the four gas circuits being , With a pressure-volume graph similar to that shown in FIG. 24, where the PV graph 180 of the compressed space is larger than the PV graph 182 of the expanded space (ie, the cooling mode).

  An alternative design of the screw mechanism is shown in FIGS. 25, 26 and 27, all of which can be used in place of the two-lobe twin screw mechanism 116, 118 described in the exemplary embodiment of the present invention. Those skilled in the art will appreciate that modifications to the corresponding internal and external fluid connections, conduits and fluid outlets for and between the "cold" and "thermal" units are possible without departing from the inventive concept of the invention. It will be understood that For example, a multi-block screw mechanism is shown in FIG. 25 where a single common male or female rotor 202 is arranged between corresponding male and female rotors 204 and 206.

  Additionally, a variety of different rotor lobe geometries and profiles can be used in the Stirling cycle apparatus, eg, the phase angle between the compression and expansion working spaces produces an adequate cooling / heating performance or mechanical work output If suitable to do so, a screw with more than two lobes can be used. Furthermore, the rotor and the lobes can be formed with different diameters and / or lengths, for example, a twin screw rotor in the "cold" unit is larger than or larger than a twin screw rotor in the "warm" unit Conversely, it can be small and power, cold or heat generation can be amplified with a relatively small temperature difference between the heat source and the heat sink.

  FIG. 26 shows an example of a two twin screw mechanism 300 with a three lobe rotor 302 and FIG. 27 shows an example of a two twin screw mechanism 400 with a four lobe rotor 402. The mid-section of the male shaft (rotary valve mechanism) can have an additional set of corresponding conduits (e.g., adding a set of corresponding conduits per additional lobe to each individual), each having an expansion part and a compression part The sum of the pair of chambers at can be divided into two corresponding working spaces so as to produce the necessary periodic volume fluctuations of gas compression / expansion due to shaft rotation. Further, it should be understood that the additional set of working spaces (e.g., from the additional chamber formed by the additional lobes) will result in the formation of an additional gas circuit.

  In another alternative embodiment of the present invention, the drive connection assembly can have an alternative valve mechanism 502 as shown in FIGS. 28-30 (a), (b). In this alternative valve mechanism, it extends over the first circumferential segment of the outer surface of the drive shaft 506 and is axially spaced from one another and circumferentially partially at respective corresponding predetermined first axial positions. An extending first fluid channel 504 is provided, and extends over a second circumferential segment of the outer surface of the drive shaft 506, axially spaced from each other and circumferentially at respective corresponding predetermined second axial positions. The second circumferential channel is provided radially opposite the second circumferential segment, and each of the first axial positions has a second axis. Each of the directional positions is axially offset. Further, a first fluid conduit 510 and a second fluid conduit 512 are provided on the drive shaft 506. Each of the fluid conduits 510, 512 has two fluidly coupled outlet ports 511, 513, the first outlet port 511 being fluidically coupled to one of the first fluid channels 504 and also the second outlet port 513. Is fluidly coupled to one of the first fluid channels 508. The fluid connections 514 are disposed in a casing 516 that surrounds the drive shaft 506 and each fluid connection 514 is a fluid to one of the first fluid channel 504 or the second fluid channel 508 during rotation of the drive shaft 506. The connection may be temporarily formed.

  Another alternative embodiment 600 of the present invention is shown in FIG. 31, where scroll mechanisms 602, 604 are used instead of the twin screw mechanism described above. This operating principle is the same as described for the embodiment having a twin screw rotor, ie to synchronize the shaft rotation in the "cold" unit 604 with the shaft rotation in the "warm" unit 602, the "cold" unit 604 There is an optimal phase angle between the working space variation of the "warm" and the working space variation of the "warm" unit 602. The actuation process can be illustrated by the graphs shown in FIGS. 20-23, but it should be understood that the cycle completion requires two or more shaft circumferential rotations.

  Furthermore, in other alternative embodiments (not shown), different compression / expansion mechanisms (eg, scroll and twin screw) can be combined. However, it should be understood that the volume fluctuations (following a linear or non-linear sawtooth function) are synchronized to form a closed regenerative Stirling cycle.

  Furthermore, the connection of the volumes in the embodiment can be similar to a twin screw rotor when utilizing a rotary conical screw mechanism.

  In addition, the multi-stage configuration of the invention (in the cooling mode) can be used to achieve even lower temperatures, as is possible with the above-described embodiments. Additionally, the Stirling cycle machine of the present invention can be provided as flat, box, cylindrical and other types. As noted above, the heat exchanger or at least a portion of the heat exchanger may be incorporated into at least a portion of the casing or rotor shaft to reduce the size of the inventive Stirling cycle device. Alternatively, part of the casing or shaft can be used as one of the heat exchangers.

  Those skilled in the art will appreciate that the embodiments described above are described by way of example only and are not meant to be limiting and that various modifications and changes may be made without departing from the scope of the invention as defined in the claims. It will be understood that it is possible.

102 "expansion" or "cold" unit 104 "compression" or "warm" unit 106 compressor mechanism 108 expander mechanism 110 "cold" heat exchanger 112 regenerator 114 "warm" heat exchanger 116 two screw mechanism 118 two axes Screw mechanism 120 2-screw rotor (male)
122 Twin screw rotor (female)
124 Compression part 126 Expansion part 128 Compression part 130 Expansion part 132 Single drive shaft 134 Single drive shaft 136 Enclosure 138 Box (transmission)
140 casing 144 conduit 146 conduit 148 conduit 150 conduit 152 fluid port 154 first outlet 156 second outlet 158 fluid channel 160 fluid channel 161 seal ring 162 fluid connection portion 164 pipe 166 compression volume fluctuation 168 expansion volume fluctuation 170 first working space 172 Second working space 202 single common male or female rotor 204 male rotor 206 female rotor 300 two-screw mechanism 302 three-lobe rotor 400 two-screw mechanism 402 four-lobe rotor 502 valve mechanism 504 first fluid channel 506 drive Shaft 508 second fluid channel 510 first fluid conduit 511 outlet port 512 second fluid conduit 513 outlet port 514 fluid connection 516 casing 602 scroll mechanism ("warm" unit)
604 Scroll mechanism ("cold" unit)

Claims (22)

In the Stirling cycle device,
A sealable housing,
A first rotational displacement unit is in fluid communication with a second rotational displacement unit, each unit operably mounting each unit in a separate fluid tight portion in the housing, at least one thermodynamic state of the working fluid during use The first and second rotational displacement units adapted to generate a periodic change of a parameter, each of the first and second rotational displacement units being
A compressor mechanism having a first compressor working chamber which can accepted the first part of the working fluid, and a second compressor working chamber capable accepted a second portion of said working fluid, said first compressor working chamber Said compressor mechanism having a first outlet port and said second compressor working chamber having a second outlet port,
A expander mechanism includes a first expander working chamber of the first can accepted the portion, and a second expander working chamber which can accepted the second portion of said working fluid of said working fluid, said The expander mechanism, wherein the first expander working chamber has a first inlet port, and the second expander working chamber has a second inlet port.
A drive coupling assembly operable to operatively couple the first expander mechanism to the first compressor mechanism,
The rotation of the first and second rotational displacement units between the first compressor working chamber and the first expander working chamber, and between the second compressor working chamber and the second expander working chamber The drive coupling assembly having a rotary valve mechanism capable of causing a predetermined sequence of periodic fluid exchange at predetermined intervals of an angle,
The first and second rotational displacement units, including
An actuator operatively coupled to the first and second rotational displacement units, wherein the rotational movement of the first rotational displacement unit is linked to synchronize with the second rotational displacement unit, thereby using Wherein the first predetermined period change of the at least one thermodynamic state parameter of the working fluid is offset by a predetermined phase angle with respect to the second predetermined period change of the at least one thermodynamic state parameter of the working fluid The actuator, which can be
, A Stirling cycle device. In Stirling cycle apparatus according to claim 1, wherein the drive pivotal coupling assembly further comprises at least one drive movement shaft, the configured inner wall to operably surround pre Symbol least one driving dynamic shaft A Stirling cycle device having at least one first shaft casing.   The Stirling cycle device according to claim 2, wherein the at least one first shaft casing extends over the first circumferential segment of the inner wall and is provided at a corresponding predetermined first axial position, and the axis A plurality of first fluid channels spaced apart from one another in the direction and partially extending in the circumferential direction, and extending over the second circumferential segment of the inner wall, provided at corresponding second predetermined axial positions respectively And a plurality of second fluid channels axially separated from each other and partially extending in the circumferential direction, and the first circumferential segment is radially opposite to the second circumferential segment. And the first axial position is axially offset from each of the second axial positions. Le devices.   4. A Stirling cycle device according to claim 3, wherein the first fluid channel and the second fluid channel spaced apart from each other in the axial direction and partially extending in the circumferential direction exist over an angle greater than 180 °. Stirling cycle device.   The Stirling cycle device according to any one of claims 2 to 4, wherein the at least one drive shaft has a first conduit having a first opening fluidly connected to the first outlet port and the first inlet. A first set of two mutually corresponding conduits comprising a second conduit having a first opening fluidly connected to the port, each of the corresponding first and second conduits being in a predetermined first radial direction It has two second openings axially adjacently connected to each other so as to radially exit the drive shaft at an angle, and one of the two second openings axially connected to each other is The other of the two second openings which are in fluid communication with one of the plurality of first fluid channels and are axially adjacently connected to each other; It is intended to engage one fluidly among the plurality of second fluid channel, Stirling cycle devices.   6. The Stirling cycle device of claim 5, wherein the at least one drive shaft is fluidly connected to a first conduit having a first opening fluidly connected to the second outlet port and to the second inlet port. The at least a second set of two mutually corresponding conduits comprising a second conduit having an aperture, each of the corresponding first and second conduits being a radius from the drive shaft at a predetermined first radial angle The first fluid having two second openings axially adjacently connected to each other so as to exit in the direction, one of the two second openings axially adjacently connected is the plurality of first fluids The other of the two second openings which are in fluid communication with one of the channels and which are axially adjacently connected to each other are the plurality of second ones. It is capable engages one fluidly engaging among the body channel, Stirling cycle devices.   7. The Stirling cycle device of claim 6, wherein each of the plurality of first fluid channels is in fluid communication with a corresponding one of the plurality of second fluid channels and, in use, with the first compressor working chamber A Stirling cycle device that enables heat exchange between a first expander working chamber and the second compressor working chamber and the second expander working chamber to be performed in a predetermined sequence.   8. The Stirling cycle apparatus according to claim 7, wherein the first compressor operating chamber and the first expander operating chamber fluidly connected in the first rotational displacement unit, and the second compressor operating chamber and the fluidly connected second compressor operating chamber. 2. A Stirling cycle device, wherein a first working space and a second working space are formed for each of the two expander working chambers.   9. The Stirling cycle device according to claim 7, wherein the first compressor operating chamber and the first expander operating chamber fluidly connected in the second rotary displacement unit, and the second compressor operating chamber fluidly connected. A Stirling cycle device, wherein a first working space and a second working space are formed for each of the second expander working chamber and the second expander working chamber.   The Stirling cycle device according to claim 9, wherein the first working space and the second working space of the first rotational displacement unit correspond to the first working space and the second working space of the second rotational displacement unit, respectively. A Stirling cycle device in fluid communication with the working space.   The Stirling cycle device according to any one of claims 7 to 10, wherein each of the correspondingly fluidly connected first fluid channel and the second fluid channel of the first rotational displacement unit is the second rotation. A Stirling cycle device in fluid communication with one fluid channel corresponding to each of the correspondingly fluidly connected first fluid channel and the second fluid channel of a displacement unit.   12. The Stirling cycle device according to claim 11, wherein each of the correspondingly fluidly connected first fluid channel and the second fluid channel of the first rotational displacement unit and the corresponding fluid of the second rotational displacement unit. Fluid communication between each of the connected first fluid channel and the second fluid channel is performed by any one or any series of a first heat exchanger, a regenerator, and a second heat exchanger. Stirling cycle device having a combination.   The Stirling cycle device according to claim 12, wherein the first heat exchanger can supply heat to the working fluid, and the second heat exchanger can remove heat from the working fluid. Is a Stirling cycle device.   The Stirling cycle device according to claim 12, wherein the regenerator fluidly connects the first heat exchanger and the second heat exchanger.   The Stirling cycle device according to any one of claims 12 to 14, wherein the first heat exchanger is an integral part of the first rotational displacement unit, and / or the second heat exchanger is A Stirling cycle device, which is an integral part of the second rotational displacement unit.   The Stirling cycle device according to any one of claims 1 to 15, wherein each of the first rotational displacement unit and the second rotational displacement unit has a twin screw mechanism.   The Stirling cycle device according to any one of claims 1 to 15, wherein each of the first rotation displacement unit and the second rotation displacement unit has a scroll mechanism or a rotation conical screw mechanism.   The Stirling cycle device according to any one of claims 1 to 15, wherein each of the first rotational displacement unit and the second rotational displacement unit is any one of a biaxial screw mechanism, a scroll mechanism, and a rotational conical screw mechanism. A Stirling cycle device having one.   The Stirling cycle device according to any one of claims 1 to 18, wherein the actuator includes a motor and a transmission capable of synchronously driving the first and second rotational displacement units. .   19. A Stirling cycle device according to any one of the preceding claims, wherein the actuator comprises a motor and a transmission which can be powered by any one of the first and second rotational displacement units. Has a Stirling cycle device.   The Stirling cycle device according to any one of claims 1 to 20, wherein the compressor mechanism and the expander mechanism of the first rotational displacement unit, and the compressor mechanism and the expander mechanism of the second rotational displacement unit, respectively. A Stirling cycle device provided in a separate and sealed part of the housing.   A Stirling cycle device according to any of the preceding claims, wherein the first rotational displacement unit is a compression unit and the second rotational displacement unit is an expansion unit.

Images